Cam-controlled twenty-four-speed mechanism



D. C. KLAUSMEYER CAM SONTROLLED TWENTY-FOUR SPEED IIECHANISII Oct. 2,1928.

2`Sheets-Sheet Filed Kay 5, 1925 ,Ivar/$15;$155,155,555.il farfalla Oct.2, 1928.` ,686,383

D. c. KLAUSMEYER CAM CONTROLLED TWENTY-FOUR SPEED MECHANISK Filed lay 5.1925 -z sheets-sheet 2 Parental oa. 2, 1928. u UNITED STAT LarissaYDAVID C. KLAUSMYEB, F CINCINNATI, OHIO, ASSIGNOB TO THE CINCINNATI BICK-FORD TOOL COIPANY, OF CINCINNATI, OHIO, A CORPORATION OF OHIO.

CAM-CONTROLLED TWENTY-FOUR-SPEED MECHANISM.

Application led 'lay 5,

This invention relates to machine-tools and it deals more particularlywith improved means for giving to a suitably' journaled shaft, rotationat any one of a considerable b number of speeds from a single speed n aprime mover. The invention may be utilized for any one of many purposesin connection with machine tools, such for example, asfor rotating thespindle of a drill- 'l0 ing and tapping machine or for actuatingy thespindle translating mechanism thereof.

u For convenience, it will be described in connection with thelast-named mechanism but it is to be understood that this is merely oneembodiment of the invention yand that the invention also contemplatesall of the various other uses for which a mechanism of this nature isadaptable. v

The tool spindle of drillin .andtapping 20. machines is adapted to carrydrillsand taps of various diameters and inasmuch as each of these toolsrequires a diii'erent speed of rotation and also-a different rate offeed, for maximum eiliciency, it is essential that meansbe rovided forroducin these varv ing spee s. Also it 1s desira le that the means forproducin these various speeds be as simple as possi le in constructionand that the means for controlling the speeds produced be readilyaccessible to the operator and adapted readily to be manipulated withoutconfusion to produce any desired speed.

This invention therefore has for an object ,to render available amultiple speed "mechanism capable of being manlpulated to -produce anyavailable s eed by a single level` readily accessible to the operatorand adapted to be shifted in vaccordance with indicia rovided by anindex 'plate adjacent the ever. Y

Another object of the invention is to provide' a multiple s eedmechanism comprising a plurality o shiftable and non-shift ablegear'units and to provide an improved camv controlled shifting mechanismfor certain of the shiftable gear-units.

Another object is to provide an improved index plate b the aid' of whichthe operator readily may advised as to the extent of axial feed of thetool per revolution of the tool spindle in all of the various operativepositions of the lever. i

Still another object of the invention 1s to provide a feed index plateby the aid of 1925.' Serial No. 28,214.

which the operator may, withv great facility` and without calculation,readily set the lever tothe proper position to effect the necessary gearsetting so to coordinate the speed of rotation of the spindle with itsaxial feed as to adapt the machine to tap; any one of certain standardthreads.

Other objects and advantages will be in part indicated in the followingdescription and in part rendered apparent therefrom in connection withthe annexed drawings.

To enable others skilled in the art so fully to apprehend the underlyingfeatures vhereof that they may embody the same in the various Wayscontemplated by this invention, drawings depicting a preferred typitzalconstruction have been annexed as a part of this disclosure and,in suchdrawings, like characters of reference denote corresponding partsthroughout all the views, of which :f-

Fig. 1 is a sectional development of the improved multiple speedmechanism as utilized to actuate'aspindle feed mechanism. Fig. 2 is aplan of the mechanism illustrated in Fig. 1 with the parts in theirnormal operative positions. Fig. 3 is a development of fill the gearshifting cams, the intermediate. cam I being shown as shiftedapproximately 180 degrees to bring the starting points of all of thecams in the same vertical line more clearly to illustrate thefunctioning of the cams. Fig. 4- is a detail showing means for throwingout a manual feed when the power means is rendered effective totranslate the spindle. Fig. 5 is a face view of the feedplate used inconnection with thefeed-controlling lever to indicate the feed in thousandths of an inch per rotation of the prime mover. Fig. 6 is adiagrammatic view illustrating the flow of motion through the changegears, selectively to produce any one f twenty-four speeds.

enter and emerge from the Work; the rate of' feed being determined bythe size and type of tool being used and the nature of the work beingoperated on. Inithe drawings S designates the spindle formed in itslower end with a socket :1: adapted to receive any one of the toolsommonlyused in this type Referring more particularly to the draw- A'ings, the invention is illustrated as embodied liu of machine tool. AnySuitable means may be employed to rotate the spindle and inasmuch as thespindle rotating means forms no part of this invention illustration anddescription thereof is deemed unnecessary.

During the rotationfof thespindle, it is necessary that the spindle bemoved lengthwise for purposes hereinbefore described. This may beeffected by having the spindle -rotatablyibut non-translatably journaledin a sleeve 1 provided with a rack 2 with which meshes an actuatingpinion 3 secured upon a shaft 4 journaled transversely to the spindle. Aworm-wheel 5, also secured upon the shaft 4, is driven by a worm 6 fixedupon a power delivery shaft 7 adapted selectively to be rotated at anyone of a plurality of speeds by means later to be described. v

Power to actuate the spindle feed mechanism may be provided by anysuitable rime mover, such for example, as a gear secured upon a suitablespindle driving sleeve D. Power from the prime mover flows to the powerdelivery shaft through three separate speed change mechanisms A, B and Caffording respectively two, four and three speed changes which togetherrender available twenty-four speeds in the power dei livery shaft. Thespeed change device A includes a gear-unit 8 splined upon a shaft 9journaled parallel with the spindle and adapted to el driven from thegear through a gear 10 fixed to said shaft, and permanently in mesh withsaid gear P. The gear-unit 8 provides gears a and b adapted selectivelyto be meshed with gears c and d, respectively, provided by a gear unit11 rotatably journaledon a shaft 12 parallel with the shaft 9. i'

The speed change device B comprises gears 0, e, f and g provided by thegearunit 11 and gearst-c', and iL-7c provided by gear units 13 and 14splined upon a sleeve 15 rotatably journaled on the power delivery shaft7. The sleeve 15 carries a gear Z constituting the initial gear of thespeed change device C. This ear is maintained permanently in mesh with agear m provided by av gear-unit 16, rotatably journaled on the shaft 12,and is'also adapted to he engaged by a clutch element n provided by ashiftable gear-unit 17 splined to the power' delivery shaft 7. Thegear-unit 16 also provides a gear o adapted to be meshed with `a gear pforming a part of the gear-unit 17. A gear g is rotatably journaled onthe shaft 12 and is adapted to be meshed with a gear '1- provided bytheL gear unit 17 The gear q is, in effect, a partof the gear unit 16and may be made integral therewith, but, for convenience of manufactureand assembling, it preferably is made as a separate part and connectedtherewith by means of clutch elements s and t.

Means, later to be described, is provided for shifting the geareunits 8,13, 14 and 17 selectively to produce any one of twenty-four speeds inthe power delivery shaft from a single speed in the prime mover. Thescheme of the transmission and the Various gear settings to produce anydesired speed in the power delivery shaft will be clearly understood byreferring to Fig. 6. The sin gle speed oin the shaft 9 passes throughthe speed change device A either through gears a and c or b and d thusdelivering two speeds to the device B. Likewise these speeds aremultiplied by four in the device l5 by causing the power selectively toow through gears 1 -h, .e-c', or g-c, thus delivering eight speeds tothe speed change device C. These eight speeds are 'further multipliedinto twenty-four speeds by the speed-change device C, by selectivelymeshing the gears thereof so that power may flow through any one of thethree courses now to be described. By shifting 'the gear-unit 17upwardly so as to enga e it directly with the sleeve 15 power will ecaused to flo through gear Z and clutch n. carried by the gear unit 17splined to the power delivery shaft thus delivering to the shaft 7 theeight speeds produced by the devices A and B. Eight additional speedsmay be obtained through gears Z, m, o and p. Still another' eight speedsare available through gears Z, m, g, and r.

As hereinbefore stated this invention pro-v vides a single shiftingdevice for all of the gear-units 8, 13, 14 and 17. This shifting devicecomprises al lever 18 fulcrumed at 19 in a yoke 20 projecting laterallyfrom a. sleeve 21 rotata ly journaled in a stationary framework 22.Splined within the sleeve 21 is a shaft 23 formed with a rack 24maintained permanently in mesh with a. segment 25 on the lever 18. Fixedu on the upper end of the shaft 23 is a gear vsllfifter 26, preferablyin thc form of a semi-circular disk which engages an annular groove 27in the gear unit 17. Thus it will be seen that vertical movement of thelever 18 about its fulcrum 19 will, through the segment 25 and rack 24,cause'the shaft 23 to be shifted axially and the ,shifter 26 will movethe gear unit lengthwise of the power delivery shaft 7 selectively toengage the clutch n and the gear Z, the gears o and p or the gears andr. Due to the cdnstruction of the shi ter 26, the shaft 23 may be givena half rotation, for purposes later to be explained, without disturbingthe operative connection between the shifter 26 andthe gear-unit 17.

' The gear-unit \is engaged by a shifter 28 translatably mounted) on a'shaft 29 carried by the stationary frame. The gear-units 13 and 14 areengaged by Shifters 3() and 31 respectively likewise translatablymounted on a shaft 32 held in the stationary frame. Theshifters 28, 30and 31 carry studs or lltl rollers 28, 30s and 31", respectively, whichtrack cam grooves 33, 34 and 35 formed in a rotatable cam cylinder 36.In Fig. 1 the cam cylinder isy shown in full lines atthe right of thefigure and in dotted lines at the .p left thereof more clearly to showthe connection between the shifter 28 and its actuating cam groove 33.It will readily be perceived that rotation of the cam cylinder 36 willthrough the cam grooves, cause-the shifters 28, 30 and 31 to betranslated thereby shifting the gear units so to mesh the gears as toproduce anyone of the'available speeds. The Shifters a ce preferablyformed ries an elongated gear 38 lheld .to rotate synchronously with thecam cylinder 36. A gear segment 39, fixed to the shaft 23 and preferablyformed inte al with the gear.

shifter 26, meshes with t e gear 38 and acts, upon rotation of the shaft23 to rotate the said gear and the cam cylinder. .Thus it will be seenthat by moving the lever 18 in a horizontal plane, about the axis of theshaft 23, it will, through the yoke 20 and sleeve 21, cause rotation ofthe Shaft 23, segment 39, gear 38 and cam cylinder 36 to shift the gearunits 8, 13 and 14 to produce eight speeds in the sleeve 15. The gearunit 17 may be shifted. vertically to multiply by threethe eight speedsdelivered thereto, by

- vertical movement of the lever 18 as hereinbefore described. It is tobe understood that the lever 18 may be moved horizontally to eightoperative positions to effect the eight speeds rovided in the speedchange devices A and and to three vertical positions to effect the threespeeds provided inthe device C. As shown more clearly in Fig. 2, thepitch radius of the gear segment 39 is substantially greater than thepitch radius of the gear 38 and therefore a one-halfro- Itation of thesegment will give the gear and the cam cylinder more than one completerotation. The cam grooves 34 and 35 are continuous about the peripheryof the cam cylinder but the cam groove 33 is non-con-4 tinuous andextends once and seven-tenths about the lcam c linder.

Referring to ig. 2, it will be seen that the pin 28a enters its camgroove 33 at the dialnetrically opposite side ofthe cam cylinder fromthe pinf30a and therefore it is lto be understood that the startingpoint of the guiding the Shifters ing point of the grooves 34 and 35.For the purpose of more clearly setting forth the coordination andfunctioning of the cams, in Fig. 3 the cam 33 is shown as shifted 180degrees about the cam cylinder to bring the starting points of all ofthe cams on the same vertical line.

Referring novvr to Fig. 3 in which the entire cam cylinder is showndeveloped and for convenience of description is shown as divided intoten equal ldivisions, the starting points of the cams, 33, 34 and 35 areindicated by 33S, 34s and`35s respectively.

The lever 18 is adapted to be moved horizontally about l8r) degrees'andthis-motion, through the segmentv 39 and gear 38, gives to the camcylinder one and seven-tenths rotations. Now considering that theleveris at one of its extreme horizontal positions, that the pins 28a, 30 and31a are in their starting positions 33s, 34s and 35s in the cams 33, 34and 35, and the lever subsequently is swung about the axis of the shaft23 in the direction to rotate the cam cylinder in the directionindicated by the arrow in Fig. 3, the action of the cams to shift thegears of the devices A and B will be as follows z- The pin 28g1 is nowin the lowermost effective run 33a of the cam 33 and thereforethe gear bis in engagement with the gear d,

(which engagement it maintains for eighttenths of'a rotation of the camcylinder, or until the pin 28a reaches the point 33b of the cam 33). Thepins 30a and 313 are in the neutral portions of the cam grooves 34 and35 respectively. A one-tenth rotation of the earn cylinder causes the-cam groove 35 Ato shift the stud 31el to the position 35b Which causesthe gear unit 14 to be shifted downwardly to mesh ,the gears g and 71,thereby eifecting a drive through the speed change devices A' and Bthrough gears b-A-Z--g-c (see Fig. 6). A further two-tenths rotation ofthe cam cylinder will then cause the stud 31a to be shifted through theneutral position 35c to the effective point 35d which Vcam groove 33 is1 8() degrees from the startcauses the gear unit 14 to be shiftedupwardly and effecting a drive through b--clf-y'. It is to be noted thatduring this movement thel stud 28a continues to track the lowereffective run 33aiand the stud 30 is tracking a neutral portion of thecam groove 34. A further two-tenths rotation of the cam cylinder shiftsthe stud 31a through the position 35e'. (which causes the gear unit 14to be shifted 'to' its neutral position) and the stud '30a is moved tothe position 34b in thc cam groove 34\.`,thereby shifting the gearunit13 downwardly and effecting a drive through the gears b-d-e-z'. Anothertwo-- tenths rotation of the cam-cylinder shifts thelstud 30a throughthe neutral position 34c in the cam groove 34 to the position 34d,thereby shiftingthe gear unit 13 upwardly,

spectively, as previouslf7 engaging the lgears a-h and effecting athree-tenths rotation of the cam shifts the stud 34EL .through theneutral portion 34e of the cam 34 and shifts the stud 28a from theeii'ective run 33, through the neutral point 33C, and into'the uppereffective run 33d, thereby shifting the gear unit 13 to its neutralposition and shifting the gear unit 8 upwardly to mesh the gears a. andc.

It is to be observed that the cam cylinder has now received one completerotation and the cam grooves 34 and 35 have each performed its completeoperation, that is successively to shift the gear units 13 and 14,respectively, to their two operative positions, while the portion 33 oft e cam groove 33 maintained-the gears b and d in mesh, there,- bycombining the four speed changes afforded .by the lspeed device B withthe gears b and d of the device A. The stud 28a also has been shifted tothe upper eifective run '33d and in a further seven-tenths rotation ofthe cam cylinder the cam grooves 35 and 34 will lagain shift the studs31a and 30JL redescribed, again to cause gear units 14 an 13 each againto be shifted to its two effective positions; thus during this lastseventh-tenths rotation the gears gnk, f-j, e-, and c-Jt aresuccessively combined with'the gears a and c and four more speeds areprovided. This last seven-tenths rotation of the cam cylinder bringsthestuds 30a and 3l to the points 34d and 35 in the cam. grooves 34 and35, respectively, and the stud 28a contacts with the closed end 33e ofthe cam groove 33 thus preventin further rotation of the cam cylinderand iereby preventing further movement of the lever 18.

Each of the eight speeds provided by the speed change devices A'and Bmay be multiplied by three in the device C by moving the lever in avertical plane thus producing the twenty-four speeds hereinbefore denscribed. j f The gear-Shifters 26, 28, 30 and 3-1 are provided withspring detents 26, 28", 30'1 and 31d, respectively, which engagesuitable notches to prevent accidental movement of the Shifters. Asshown vin Fig. 1 the detent 26d' is adapted to engage any one of fourdetent notches 26e, 26, 26g or 26u'. The notches 26, 26t and 26gcorrespond to lower, intermediate and upper. operative positionsrespectively of the gear-unit 17 and the notch 26u corresponds to theneutral position of said gear unit 17, that is with the gears p and rintermediate the frearso and q. In'addition to the hereinbefbredescribed wer drive for the worm 6, means also isprovided whereby theworm may be rotateclmanually and this manual drive is so coordinatedwitli'the power drive Y that they both may not be effective at the sametime.

This is' accomplished by providing automatically acting means to holdthe manual means out of action whenever the power feed is ef#- fectiveand to connect the manual means when the power feed is thrown out. Tothat end, a clutch element 40 is liXed to the shaft 7, and this clutchelement is adapted, at certain times, to be engaged by a similar clutchelement 41. This latter clutch element is carried by a shaft 42 which istranslatably mounted in the hub 43 of a hand wheel 44, rotatably'ournaled in a bearing 45 with its axis coinci ent with the axis of theshaft 7. A spring `46 interposed between the shaft 42 and a screw 47threaded into the hand-wheel normally tends to move the shaft y42axially to engage the clutch members 4() and 41. The clutch member 41and shaft 42 may be shifted'against the action of the spring 46 by meansof a bell-crank lever 484 fulcrumed at l49. One arm ofthe lever 48carries a shoe 50 which tracks a groove 51 inthe clutch element 41 andthe other" arm carries a. contact point 52 whiclrbears against the perihery of the shaft 23 under the action o the spring 46. The shaft 23 isformed with an annular notch 53 into which the point 52 drops when the"lever 18 and the shaft 23 are in their neutral positions. The notch 53is formed withnpper and lower inclined walls 53?- and 53'which, when theshaft 23 is moved axially from its neutral point, act as cams on thepoint 52, and cause the lever 48 to be iswun about its fulerum todisengage the clutch lements 40 and 41. From the foregoing it will beperceived that either the manual drive or the power drive may berendered effective but that they both may not be effectivesimultaneously.

Another important tion resides in the em loyment of the s eciallydesigned index p ate 60, shown in ig. 5, in combination with the singlegear shifting lever 18. This index plate is supported by a stationaryart of the tool-head, concentric with the sha t 23,' and is divided intothree horizontal rows y'and z of indicia corresponding to the threevertical-positions 18x, 18? and 18' of the lever 18 (see Fi 1). Each ofthese three rows is divide into eight sub-divisions corresponding to thefeature of this inveneight horizontal positions of the lever 18 bothvertically andhorizontally acrossl provided by eachof' the subdivisionsprefy erably indicate the feed in thousandths of an inch'per rotation of the spindle. This is feasible because of the fact that the primemoverfor the feed is operatively'connected with the spindle and therefore thespeed of rotation of the spindle and the feed therefor are coordinatedand by setting the pointer 61 to any one of the subdivisions on theindex plate the gears of the speed change devices A, B and C will be someshed'as to thrown in as hereinbefore described.

As is well understood, these machine tools A are also used for tappingand therefore in fact.

order to tap a hole with a standard thread, it is necessary that only acertain predetermined feed be employed. For example, the standard screwthread for a one-inch hole 4is eight threads per inch, therefore if itis desired to tap such a hole it is necessary that the tap be advancedone-eighth of an inch or .125 inch) for each rotation thereof. In thatcase, the lever 18 would be shifted to bring the tip of the pointer tothe subdivision a which is marked 125F indicating a feed of .125 inch'per rotation of the tool spindle. j

To enable the operator readily and without calculation to shift thegears to produce any available standard tap lead, those subdivisionswhich produce spindle feeds, corresponding to the various standard tapleads, also contain indicia to indicate that For instance, thesubdivisions e also contains the marking 8T which indicates that whenthe pointer is brought to that subdivision the gears will be so meshedas to tap eight threads per inch.

Still further to assist the operator in selecting the settings whichproduce the standard ltap leads the subdivlsions which indicate suchsettings are preferably of a color in contrast with the color ofthesubdivisions which do not indicate a standard tap lead and whichare usedprimarily for drilling feeds. For example, the subdivisions a', e2, e3,24 z5, es, y and the instruction subdivision 'v may have a back groundof black and the remainder of the subdivisions and the blank w may havea back ground of red, but any other contrastin colors may be used. Forconvenience, t e tap feed subdivisions are shown in black and the drillfeed subdivisions are shownin white, but

`it is toy be understood that these colors are vonly representative.

From the foregoing, it will be perceived that others that this inventionprovides a very simple v and efficient means 1n the form of a singlelever for shifting all four of the shiftable gear units. It will also beseen that by utilizing the cam grooves 34 and 35 twice, the diameter ofthe cam cylinder may be iliade substantially smaller than if the usualpractice was followed and each cam groove was used only once in acomplete gear shifting cycle. This reduction in size and the consequentcompactness of parts secured thereby is of great importanceinasmuch asmuch mechanism is embodied in these drillheads and very little space isavailable. Furthermore, it will be perceived'that the new feed platewill greatly assist the operator in effecting the proper .setting of thegears and fewer mistakes will be made than heretofore.

Without further analysis, the foregoing will so fully reveal the gist ofthis invention can, rby applying current knowledge, readily adapt it forvarious utilizations by retaining one or more of the features that,from' the standpoint of the prior art, fairly constitute essentialcharacteristics of either the generic or specificaspects of thisinvention and, therefore, such adaptations should be, and are intendedto be, comprehended within themeaning and range of equivalency of thefollowing claims.

Having thus revealed this invention, I

claim as new and desire to secure the following combinations andelements, or equivalents thereof, by Letters Patent of the United Statesl. A multiple speed mechanism combining a prime-mover; a rotatablemember; means operatively connectingv said prime mover with saidrotatable member, said means including a plurality of shiftable gears;means to shift said gears selectively to produce any one of a pluralityof drives between said prime mover and said member,

said gear shifting means comprising a lever movable in transverseplanes; a rotatablyv and translatably mounted shaft; two operativeconnections between said lever and said shaft, whereby movement of saidlever in one plane rotates said shaft and movement of said lever inanother plane translates said shaft; a gear' shifter secured to saidshaft and adapted to shift one of said shiftable gears b the axialmovement of said shaft; a rotatab e cam operatively connected to actuateanother of said gear Shifters; and an operative connection between saidshaft and said cam to cause said cam to be rotated by the rotarymovement of said shaft.

2. In a multiple speed mechanism including a plurality of shiftablegears; a plurality of gear-Shifters each operatively connected with oneof said gears; a shaft upon which one of said gear-Shifters is secured;means to move said shaft axially to cause Saidlast named gear-shifter toshift one of said gears; a rotatable cam operatively connected toactuate another of said gear-shift ers; a gear rotatable with said cam;a gearsegment meshing with said gear and opera-- tively connected withsaid shaft; and means to rotate said shaft to cause said segment torotate said last named gear thereby to cause said cam to actuate one ofsaid gear-Shifters.

3.4 In a multiple speed mechanism including a plurality of shiftablegear-units; a shaft adapted to be rotated and translated; a ear-shifterand a gear-segment secured to said shaft and movable axially androtatively therewith; a gear-unit engaged by said gear-shifter andadapted to be actuated by the axial movement of said shaft; a gearmeshing with said segment and adapted to be actuated by the rotativemovement of said shaft and segment; a cam rotatable with said gear; agear-shifter actuated by said cam and adapted to shift one of said gearunits; and means to rotate and translate said shaft. y

- 4. In a multiple speed mechanism includling a plurality of shiftablegear-units; a

shaft adapted to be rotated and translated' a `gear-segment 'and agear-shifter secure to said shaft and movable axially and rotativelytherewith; a gear-unit engaged by said gear-shifter and Aadapted to bemoved by the axial; movement of said shaft; a gear meshing with saidsegment and'adapted to be. rotated by the rotative movement of saidshaft; a gear-shifter engaging one of said shiftable gear-units andadapted to be actuated by the rotar movement of said gear; a rack onsaid sha a member mounted coaxial with ysaid shaft and rotatabletherewith; a lever fulcrumed on said member; a gear-segment provided bysaid lever and adapted to mesh with said rack, said parts being soconstructed and arranged that movement of said lever about its fulcrumshifts the shaft axially and movement of the lever about the axis of theshaft rotates said shaft.

5. A drilling and tapping machine combining, a rotatable andtranslatable spindle; spindle translating means comprising a primemover,three serially arranged speed change devices connecting said prime moverwith said spindle and affording respectively two, three and four speedchanges to give to said spindle twenty-four feed rates from a singlespeed in said prime mover, each of said speed change devices includingshiftable and non-shiftable gears; gear-Shifters engaging said shiftablegears; a rotatable and translatable shaft connected with said gearShifters and adapted by rotation and translation to actuate all ofsaid'shi-fters; a single lever movable in one yplane to three positionsand ina plane transverse to the first mentioned plane to eight positionsfor each of the three first mentioned positions thereby to rotate andtranslate said shaft to effect all of saidtwenty-four feed changes; apointer carried by said lever; and an index late underlying said pointerand provide with three rows of indicia corresponding to the threepositions of said lever in one plane; each of said'rows comprising eightsymbols corresponding to the eight ositions of said lever in the otherplane, eac of said s mbols cooperating with said pointer to inicate thespindle -feed rate effected b movement of sald Alever and .pointer to te indicated position.

'In witness whereof, I have hereunto lsubscribed myname.

DAVID c. KLAUSMEVYER.

